KR101629899B1 - Rotor and rotary fluid machine - Google Patents

Rotor and rotary fluid machine Download PDF

Info

Publication number
KR101629899B1
KR101629899B1 KR1020157034744A KR20157034744A KR101629899B1 KR 101629899 B1 KR101629899 B1 KR 101629899B1 KR 1020157034744 A KR1020157034744 A KR 1020157034744A KR 20157034744 A KR20157034744 A KR 20157034744A KR 101629899 B1 KR101629899 B1 KR 101629899B1
Authority
KR
South Korea
Prior art keywords
groove
center
rotor
tubular member
resin layer
Prior art date
Application number
KR1020157034744A
Other languages
Korean (ko)
Other versions
KR20150143886A (en
Inventor
나오키 호리베
마사노리 아키즈키
히로시 카네미츠
Original Assignee
다이호 고교 가부시키가이샤
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 다이호 고교 가부시키가이샤 filed Critical 다이호 고교 가부시키가이샤
Publication of KR20150143886A publication Critical patent/KR20150143886A/en
Application granted granted Critical
Publication of KR101629899B1 publication Critical patent/KR101629899B1/en

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
    • F04C18/322—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2230/00—Manufacture
    • F04C2230/90—Improving properties of machine parts
    • F04C2230/91—Coating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/54—Hydrostatic or hydrodynamic bearing assemblies specially adapted for rotary positive displacement pumps or compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00—Material properties
    • F05C2251/14—Self lubricating materials; Solid lubricants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00—Other material characteristics; Treatment of material
    • F05C2253/20—Resin

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)

Abstract

제1 폐쇄 부재(2)와 제2 폐쇄 부재(3)는 통형상 부재(1)의 축방향의 양단의 개구부를 폐쇄한다. 기재(411)는 통형상 부재(1)와 제1 폐쇄 부재(2) 및 제2 폐쇄 부재(3)로 형성된 공간에 수용되며, 통형상 부재(1)의 축방향과 동일 방향의 축의 주위를 회전한다. 수지층(410)은 기재(411)의 스러스트면에 형성되어 있다. 홈(C)은 수지층(410)에 형성된 동심원을 이루는 복수의 고리형상 홈 또는 소용돌이형상 홈으로서, 당해 고리형상 홈의 고리의 중심 또는 당해 소용돌이형상 홈의 소용돌이의 중심이 기재(411)의 회전 중심과 다르다.The first closing member 2 and the second closing member 3 close the openings at both ends in the axial direction of the tubular member 1. The base material 411 is accommodated in a space formed by the tubular member 1, the first closing member 2 and the second closing member 3 and is disposed around the axis in the same direction as the axial direction of the tubular member 1 Rotate. The resin layer 410 is formed on the thrust surface of the substrate 411. The groove C is a plurality of concentric circular grooves or spiral grooves formed in the resin layer 410. The center of the annular groove of the annular groove or the center of the spiral of the spiral groove forms the rotation of the substrate 411 It is different from the center.

Description

로터 및 로터리형 유체 기계{ROTOR AND ROTARY FLUID MACHINE}[0001] ROTOR AND ROTARY FLUID MACHINE [0002]

본 발명은 로터 및 로터리형 유체 기계에 관한 것이다. The present invention relates to a rotor and a rotary fluid machine.

실린더의 양단을 폐쇄하여 형성된 공간의 내부에서 로터와 베인(vane)을 운동시킴으로써 유체의 흡입·토출을 하는 로터리형 유체 기계가 알려져 있다. 로터리형 유체 기계에서는 로터의 눌어붙음이나 마모를 방지할 것이 요구된다. 이러한 과제를 해결하기 위한 기술로서, 예를 들어 특허문헌 1에는 실린더의 내주(內周)와 로터의 외주(外周)의 쌍방 또는 그 중 어느 한쪽에 침황 질화 처리 또는 침황 처리에 의해 개질해서 이루어진 표면 개질층을 가진 로터리형 압축기가 기재되어 있다.There is known a rotary type fluid machine in which fluid is sucked and discharged by moving a rotor and a vane in a space formed by closing both ends of a cylinder. In a rotary type fluid machine, it is required to prevent the rotor from sticking or abrasion. As a technique for solving such a problem, for example, Patent Document 1 discloses a technique for improving the surface of a cylinder, which is modified by oxygen nitrification treatment or sulfuric acid treatment on both the inner circumference of the cylinder and the outer circumference of the rotor, A rotary type compressor having a reforming layer is disclosed.

일본국 공개특허공보 2004-278309호Japanese Patent Application Laid-Open No. 2004-278309

특허문헌 1에 기재된 기술에서는 로터의 스러스트(thrust)면에 유막(油膜)이 형성되기 어렵기 때문에, 압축시의 누설 손실 및 소비 동력이 높아진다는 문제가 있었다.In the technique described in Patent Document 1, there is a problem that the oil film is hardly formed on the thrust surface of the rotor, so that leakage loss and power consumption during compression are increased.

따라서 본 발명은 로터의 스러스트면에 유막이 형성되기 쉽게 하여, 압축시의 누설 손실 및 소비 동력을 저감할 수 있는 기술을 제공한다.Therefore, the present invention provides a technique that makes it easier for oil film to form on the thrust surface of the rotor, thereby reducing leakage loss and power consumption during compression.

본 발명은 통형상 부재와 당해 통형상 부재의 축방향의 양단의 개구부를 폐쇄하는 폐쇄 부재로 형성된 공간에 수용되며, 상기 축방향과 동일 방향의 축의 주위를 회전하는 기재(基材); 상기 기재의 스러스트면에 형성된 수지층; 및 상기 수지층에 형성된 동심원을 이루는 복수의 고리형상 홈 또는 소용돌이형상 홈으로서, 당해 고리형상 홈의 고리의 중심 또는 당해 소용돌이형상 홈의 소용돌이의 중심이 상기 기재의 회전 중심과 다른 홈;을 가진 로터를 제공한다.The present invention relates to a tubular member which is accommodated in a space formed by a closing member that closes an opening at both ends in the axial direction of the tubular member and rotates around an axis in the same direction as the axial direction; A resin layer formed on the thrust surface of the substrate; And a plurality of concentric annular grooves or spiral grooves formed in the resin layer, wherein the center of the annular groove of the annular groove or the center of the spiral of the spiral groove is different from the center of rotation of the substrate Lt; / RTI >

상기 구성에서 상기 기재의 회전 중심에 대한 상기 고리형상 홈의 고리의 중심의 편심량 또는 상기 소용돌이형상 홈의 소용돌이의 중심의 편심량이 상기 홈의 피치 이상이어도 된다.The eccentric amount of the center of the annular groove of the annular groove or the eccentric amount of the center of the vortex of the vortex groove may be equal to or greater than the pitch of the groove.

또한 본 발명은 통형상 부재; 상기 통형상 부재의 축방향의 양단의 개구부를 폐쇄하는 폐쇄 부재; 및 상기 로터;를 가지는 로터리형 유체 기계를 제공한다.The present invention also relates to a tubular member, A closing member closing the openings at both ends in the axial direction of the tubular member; And the rotor.

본 발명에 따르면, 로터의 스러스트면에 유막이 형성되기 쉽게 하여, 압축시의 누설 손실 및 소비 동력을 저감할 수 있다.According to the present invention, an oil film is easily formed on the thrust surface of the rotor, so that leakage loss and power consumption during compression can be reduced.

도 1은 일 실시형태에 따른 로터리형 압축기를 나타낸 부분 단면도이다.
도 2는 도 1에 도시한 II-II선을 따라 자른 압축 기구(6)의 단면도이다.
도 3은 로터(41)의 측면도이다.
도 4는 로터(41)의 평면도이다.
도 5는 도 4에 도시한 III-III선을 따라 자른 홈(C)의 단면도이다.
도 6은 로터리형 유체 기계의 변형예를 나타낸 도면이다.
도 7은 로터리형 유체 기계의 변형예를 나타낸 도면이다.
도 8은 홈(C)의 변형예를 나타낸 도면이다.1 is a partial cross-sectional view showing a rotary compressor according to an embodiment.
Fig. 2 is a sectional view of the compression mechanism 6 cut along the line II-II shown in Fig.
3 is a side view of the rotor 41. Fig.
4 is a plan view of the rotor 41. Fig.
5 is a cross-sectional view of the groove C cut along the line III-III shown in FIG.
Fig. 6 is a view showing a modification of the rotary fluid machine. Fig.
7 is a view showing a modification of the rotary fluid machine.
Fig. 8 is a view showing a modification of the groove C; Fig.

1. 실시형태(로터리형 압축기의 구조)1. Embodiment (Structure of Rotary Type Compressor)

이하, 도면에서 로터리형 압축기(9)의 각 구성의 배치를 설명하기 위해, 각 구성이 배치되는 공간을 xyz 오른손 좌표 공간으로 나타낸다. 또한 도면에 표시한 좌표 기호 중, 안쪽이 흰 원 안에 검은 원을 그린 기호는 지면(紙面) 안쪽에서 앞쪽으로 향하는 화살표를 나타내고 있다. 또한 안쪽이 흰 원 안에 교차하는 2개의 선분을 그린 기호는 지면 앞쪽에서 안쪽으로 향하는 화살표를 나타내고 있다. 공간에 있어서 x축을 따른 방향을 x축방향이라고 한다. 또한 x축방향 중 x성분이 증가하는 방향을 +x방향이라고 하고, x성분이 감소하는 방향을 -x방향이라고 한다. y, z성분에 대해서도 상기 정의에 따라서 y축방향, +y방향, -y방향, z축방향, +z방향, -z방향을 정의한다.Hereinafter, in order to explain the arrangement of each constitution of the rotary compressor 9 in the figure, the space in which each constitution is arranged is represented by xyz right-handed coordinate space. In addition, among the coordinate symbols shown in the drawing, a symbol drawn with a black circle in a white circle inside indicates an arrow pointing from the inside to the front of the paper. Also, the symbol drawn by two line segments intersecting in the white circle inside indicates an arrow pointing from the front to the inside of the ground. The direction along the x axis in space is called the x axis direction. The direction in which the x component increases in the x-axis direction is referred to as the + x direction, and the direction in which the x component decreases is referred to as the -x direction. y, and z components are defined in the y-axis direction, the + y direction, the -y direction, the z-axis direction, the + z direction, and the -z direction according to the above definition.

도 1은 본 발명의 일 실시형태에 따른 로터리형 압축기(9)를 도시한 부분 단면도이다. 로터리형 압축기(9)는 본 발명에 따른 로터리형 유체 기계의 일례이며, 예를 들면, 자동차용, 가정용, 철도용 또는 업무용 공기 조화기(공조기)에서 냉매 가스 등의 기체 압축에 이용된다. 로터리형 압축기(9)는 밀폐 케이싱(8) 내의 상부에 수납된 구동원으로서의 모터(7); 및 밀폐 케이싱(8) 내의 하부에 배치됨과 아울러 상기 모터(7)에 의해 구동되며 냉매 가스를 흡입·토출하는 압축 기구(6);를 구비하고 있다.1 is a partial cross-sectional view showing a rotary compressor 9 according to an embodiment of the present invention. The rotary type compressor 9 is an example of a rotary fluid machine according to the present invention and is used for gas compression of a refrigerant gas or the like in, for example, an automobile, a domestic use, a railway or an industrial air conditioner (air conditioner). The rotary compressor (9) includes a motor (7) as a drive source accommodated in an upper portion of a sealed casing (8); And a compression mechanism (6) disposed at a lower portion in the sealed casing (8) and driven by the motor (7) to suck and discharge the refrigerant gas.

도 2는 도 1에 도시한 II-II선을 따라 자른 압축 기구(6)의 단면도이다. 압축 기구(6)는 이른바 로터리 베인 방식(슬라이딩 베인 방식)에 따른 압축 기구이다. 압축 기구(6)는 도 1의 상하방향(z축방향)에 축을 갖는 원통형상의 부재(이하, 통형상 부재(1)라고 함); 이 통형상 부재(1)의 아래쪽 단면(端面) 및 개구부(이하, 제1 개구부(K1)라고 함)를 폐쇄하는 제1 폐쇄 부재(2); 통형상 부재(1)의 위쪽 단면 및 개구부(이하, 제2 개구부(K2)라고 함)를 폐쇄하는 제2 폐쇄 부재(3); 및 작동부(4);를 가진다. 통형상 부재(1)는 이른바 실린더이다. 작동실(5)은 통형상 부재(1)를 그 축방향 양쪽에서(즉, 도 1의 위아래에서) 제1 폐쇄 부재(2) 및 제2 폐쇄 부재(3) 사이에 끼우고, 통형상 부재(1)의 원주방향의 복수 개소를 복수의 볼트(81)로 체결함으로써 통형상 부재(1)의 내부에 형성된다.Fig. 2 is a sectional view of the compression mechanism 6 cut along the line II-II shown in Fig. The compression mechanism 6 is a compression mechanism according to a so-called rotary vane system (sliding vane system). The compression mechanism 6 comprises a cylindrical member (hereinafter referred to as a tubular member 1) having an axis in the up-down direction (z-axis direction) in Fig. 1; A first closing member 2 for closing a lower end surface of the tubular member 1 and an opening (hereinafter referred to as a first opening portion K1); A second closing member 3 for closing an upper end surface of the tubular member 1 and an opening (hereinafter referred to as a second opening K2); And an actuating part (4). The tubular member 1 is a so-called cylinder. The operating chamber 5 is provided with the cylindrical member 1 sandwiched between the first closing member 2 and the second closing member 3 on both sides of the axial direction thereof Is formed inside the tubular member (1) by fastening a plurality of portions in the circumferential direction of the tubular member (1) with a plurality of bolts (81).

작동부(4)는 구동축(40), 로터(41), 베인(42) 및 베인 홈(44)을 가진다. 도 2에 도시한 예에서는 베인(42)이 2군데에 마련되어 있으나, 베인(42)이 마련되는 장소는 1군데여도 좋고 3군데 이상이어도 좋다. 로터(41)의 내주측에는 제1 폐쇄 부재(2) 및 제2 폐쇄 부재(3)에 각각 마련된 구멍을 지나 작동실(5)의 외부로 통하는 구동축(40)이 관통하고 있다. 구동축(40)은 모터(7)에 연결되어 있으며, 모터(7)의 구동력에 의해 구동축(40) 및 로터(41)가 D1방향으로 회전한다. 밀폐 케이싱(8) 내의 하부에는 윤활유(80)가 저류되어 있고, 로터(41)가 회전될 때는 구동축(40)의 하단부 내에 형성된 도시하지 않은 기름통로를 통해 로터(41)의 내주면과 외주면에 윤활유(80)가 공급된다.The operating portion 4 has a drive shaft 40, a rotor 41, a vane 42, and a vane groove 44. In the example shown in FIG. 2, the vanes 42 are provided at two locations, but the vane 42 may be provided at one location or at three or more locations. The drive shaft 40 passing through the holes provided in the first closing member 2 and the second closing member 3 and communicating with the outside of the operation chamber 5 passes through the inner peripheral side of the rotor 41. The driving shaft 40 is connected to the motor 7 and the driving shaft 40 and the rotor 41 are rotated in the direction D1 by the driving force of the motor 7. [ Lubricant 80 is stored in the lower portion of the sealed casing 8 and lubricant oil is supplied to the inner peripheral surface and the outer peripheral surface of the rotor 41 through an oil passage not shown formed in the lower end portion of the drive shaft 40 when the rotor 41 is rotated. (80) is supplied.

구동축(40) 및 로터(41)는 동축(同軸)의 주위를 회전하지만, 구동축(40)의 중심과 통형상 부재(1)의 내주의 중심은 다르기 때문에, 로터(41)와 통형상 부재(1)의 내주면 사이에는 도 2에 도시한 것과 같은 발굽형상의 공간(작동실(5))이 형성된다. 로터(41)에는 베인(42)을 수납한 베인 홈(44)이 마련되어 있고, 베인(42)은 배압(背壓)에 의해 베인 홈(44)에서 돌출하여 통형상 부재(1)의 내주면으로 향하는 힘을 받고 있다. 로터(41)의 회전에 수반하여, 베인(42)의 선단이 그 통형상 부재(1)의 내주면에 접하면서 베인 홈(44)을 따라 움직이기 때문에, 작동실(5)은 베인(42)에 의해서 복수의 격실로 구분지어져서 각 격실에 채워진 유체가 흡입구(13)에서 토출구(14)로 이동한다. 토출구(14)에 베인(42)이 근접하면 베인(42)에 의해 구분지어진 작동실(5)의 내압이 상승하여, 토출압을 넘었을 때에 토출 밸브(15)에 대항하여 작동실(5) 내부를 채우는 유체가 토출구(14)에서 토출된다.Since the center of the drive shaft 40 and the center of the inner periphery of the tubular member 1 are different from each other, the rotor 41 and the cylindrical member (rotor) 41 rotate about the coaxial (Working chamber 5) as shown in Fig. The rotor 41 is provided with a vane groove 44 in which the vane 42 is housed. The vane 42 protrudes from the vane groove 44 due to back pressure to the inner peripheral surface of the tubular member 1 It is receiving the power to head. The operating chamber 5 is moved in the axial direction of the vane 42 by the rotation of the rotor 41 so that the tip of the vane 42 contacts the inner circumferential surface of the tubular member 1 and moves along the vane groove 44, And the fluid filled in each compartment is moved from the suction port 13 to the discharge port 14. In this case, When the vane 42 approaches the discharge port 14, the internal pressure of the operation chamber 5 divided by the vane 42 rises, and when the discharge pressure exceeds the discharge pressure, And the fluid filling the inside is discharged from the discharge port 14.

도 3은 로터(41)의 측면도이다. 로터(41)는 통형상 기재(411); 및 기재(411)의 제1 폐쇄 부재(2) 또는 제2 폐쇄 부재(3)에 대향하는 면(이하, 스러스트면이라 함)에 형성된 수지층(410);을 가진다. 수지층(410)은 예를 들면, 폴리아미드이미드계 수지, 폴리이미드계 수지, 이들 수지의 디이소시아네이트 변성, BPDA 변성, 술폰 변성 수지, 에폭시 수지, 폴리에테르에테르케톤 수지, 페놀 수지, 폴리아미드, 엘라스토머 중 어느 1종 이상을 바인더 수지로서 함유한다. 또한 수지층(410)은 예를 들면, 그라파이트, 카본, 이황화 몰리브덴, 폴리테트라플로오로에틸렌, 질화 붕소, 이황화 텅스텐, 불소계 수지, 연질 금속(예를 들면 Sn, Bi 등) 중 어느 1종 이상을 고체 윤활제로서 함유한다. 기재(411)는 주철(cast iron)로 형성되어도 되고, 알루미늄, 스테인리스강 등 각종 재료에 대하여, 소결, 단조, 절삭, 프레스, 용접 등의 각종 가공 처리를 함으로써 형성되어도 된다. 또 기재(411)는 세라믹제여도 되고, 수지제여도 된다.3 is a side view of the rotor 41. Fig. The rotor 41 includes a tubular substrate 411; And a resin layer 410 formed on a surface of the substrate 411 facing the first closure member 2 or the second closure member 3 (hereinafter referred to as a thrust surface). The resin layer 410 may be formed of, for example, a polyamide-imide resin, a polyimide resin, a diisocyanate-modified resin, a BPDA-modified resin, a sulfonated resin, an epoxy resin, a polyetheretherketone resin, And an elastomer as a binder resin. The resin layer 410 may be formed of any one or more of, for example, graphite, carbon, molybdenum disulfide, polytetrafluoroethylene, boron nitride, tungsten disulfide, fluororesin, As a solid lubricant. The base material 411 may be formed of cast iron or may be formed by various kinds of processing such as sintering, forging, cutting, pressing and welding on various materials such as aluminum and stainless steel. The base material 411 may be made of ceramic or resin.

도 4는 로터(41)의 평면도이다. 수지층(410)에는 동심원을 이루는 복수의 고리형상 홈(C)이 형성되어 있다. 홈(C)의 고리 중심(O2)은 로터(41)의 회전 중심(O1)(구동축(40)의 축심)과는 다른 위치에 있다. 로터(41)의 회전 중심(O1)에 대한 홈(C)의 중심(O2)의 편심량은 홈(C)의 피치 1개분 이상인 것이 바람직하다(단, 홈(C)이 등간격일 경우).4 is a plan view of the rotor 41. Fig. A plurality of concentric annular grooves C are formed in the resin layer 410. The ring center O2 of the groove C is located at a different position from the rotational center O1 of the rotor 41 (axial center of the drive shaft 40). It is preferable that the amount of eccentricity of the center O2 of the groove C with respect to the rotation center O1 of the rotor 41 is equal to or larger than one pitch of the grooves C (provided that the grooves C are equal intervals).

도 5는 도 4에 도시한 III-III선을 따라 자른 홈(C)의 단면도이다. 홈(C)의 단면은 깊은 위치일수록 폭이 좁아지며 바닥에 가까워질수록 폭의 변화가 급해지는 U자 내지 반원에 비슷한 형상이다. 홈(C)은 수지층(410)의 표면을 따라서 절삭 공구의 칼날을 이동시켜서 형성된다. 홈(C)의 폭(w)은 홈(C)이 연장되는 방향에 직교하는 단면(斷面)에서의 홈(C)의 폭이고, 상기 단면에서 홈(C)의 양단부를 연결한 선분의 길이이다. 홈(C)의 간격(p)은 이웃하는 2개의 홈(C)끼리의 간격이며, 홈(C)이 연장되는 방향에 직교하는 단면에서 이 홈(C)들의 중심끼리를 연결한 선분의 길이이다. 간격(p)은 예를 들면 0.1~0.15mm이다. 이 예에서 홈(C)의 폭(w)은 홈(C)의 간격(p)과 동일하다.5 is a cross-sectional view of the groove C cut along the line III-III shown in FIG. The cross-section of the groove (C) is narrower in the deep position, and is similar to the U-shape or the half-circle in which the width changes as the position nears the bottom. The groove C is formed by moving the blade of the cutting tool along the surface of the resin layer 410. The width w of the groove C is the width of the groove C in a cross section orthogonal to the direction in which the groove C extends and the width of the groove C connecting the both ends of the groove C Length. The interval p of the grooves C is the distance between two adjacent grooves C and the length of a line segment connecting the centers of the grooves C at a cross section orthogonal to the direction in which the grooves C extend to be. The interval p is, for example, 0.1 to 0.15 mm. In this example, the width w of the groove C is the same as the interval p of the groove C.

본 실시형태에서는 수지층(410)에 형성된 산부(山部)(B) 각각과, 제1 폐쇄 부재(2) 및 제2 폐쇄 부재(3)가 선접촉한다. 여기서, 홈(C)의 중심(O2)이 로터(41)의 회전 중심(O1)과 다른 위치에 있기 때문에, 홈(C)의 각 점에서의 접선의 방향이 로터(41)의 회전방향과 다르다(단, 중심(O2)과 회전 중심(O1)을 지나는 직선상의 점은 제외함). 그러므로 쐐기 효과(wedge effect)(쐐기막 효과라고도 함)에 의해, 산부(B)와 제1 폐쇄 부재(2) 및 제2 폐쇄 부재(3) 사이에 윤활유(80)가 끌려들어가, 유막이 형성되기 쉬워진다. 따라서 본 실시형태에 따르면 홈(C)의 중심(O2)이 로터(41)의 회전 중심(O1)과 동일한 위치에 있는 경우에 비해, 수지층(410)과 제1 폐쇄 부재(2) 및 제2 폐쇄 부재(3)의 접촉 부분의 기밀성 및 윤활성이 향상된다.In this embodiment, each of the peak portions B formed on the resin layer 410 and the first closing member 2 and the second closing member 3 are in line contact with each other. Since the center O2 of the groove C is located at a position different from the rotational center O1 of the rotor 41, the direction of the tangent at each point of the groove C is different from the rotational direction of the rotor 41 (Except for points on the straight line passing through the center O2 and the rotation center O1). Therefore, by the wedge effect (also called the wedge effect), the lubricant 80 is drawn between the crest B and the first closing member 2 and the second closing member 3, . Therefore, compared with the case where the center O2 of the groove C is at the same position as the rotation center O1 of the rotor 41, the resin layer 410, the first closing member 2, 2 airtightness and lubricity of the contact portion of the closing member 3 are improved.

2. 변형예2. Variations

이상, 실시형태를 설명했으나, 이 실시형태의 내용은 다음과 같이 변형할 수 있다. 또한 이하의 변형예를 조합해도 된다.Although the embodiment has been described above, the contents of this embodiment can be modified as follows. The following modifications may be combined.

2-1. 적용예2-1. Application example

전술한 실시형태에서, 로터리형 압축기(9)가 적용되는 장치로서 자동차용, 가정용, 철도용 또는 업무용 공기 조화기를 들었지만, 냉동기, 냉장장치 등에 적용되어도 되고, 수온 조절, 항온조, 항습조, 도장 설비, 분체 수송 장치, 식품 가공 장치, 공기 분리 장치 등 각종 장치에 사용되어도 된다. 또한 상술한 실시형태에서 본 발명에 따른 로터리형 유체 기계의 일례로서 로터리형 압축기(9)를 예로 들었으나, 이 외에도, 기체를 다루는 로터리형 송풍기나 액체를 다루는 로터리형 펌프 등을 본 발명에 따른 로터리형 유체 기계로 들 수 있다.In the above-described embodiment, the apparatus to which the rotary compressor 9 is applied is an air conditioner for an automobile, a domestic use, a railway, or a commercial, but may be applied to a refrigerator or a refrigerator. , A powder transport device, a food processing device, an air separation device, and the like. Although the rotary type compressor 9 has been described as an example of the rotary fluid machine according to the present invention in the above-described embodiments, a rotary type blower for handling a gas, a rotary type pump for handling liquid, Rotary type fluid machine.

2-2. 변형예 12-2. Modification 1

도 6은 로터리형 유체 기계의 변형예를 도시한 도면이다. 작동부(4a)는 구동축(40a), 로터(41), 베인(42a)을 가진다. 구동축(40a)에는 구동축(40a) 자신과 다른 축을 중심으로 하는 원기둥형상의 편심부(도시 생략)가 마련되어 있으며, 이 편심부가 로터(41a)(이른바 롤링 피스톤)의 내주측에 끼워넣어져 있다. 그렇기 때문에 구동축(40a)이 회전하면 이에 따라 로터(41a)는 통형상 부재(1a)의 내주면을 따라서 편심 회전한다.6 is a view showing a modification of the rotary fluid machine. The operating portion 4a has a drive shaft 40a, a rotor 41, and a vane 42a. The drive shaft 40a is provided with a cylindrical eccentric portion (not shown) centered on a different axis from the drive shaft 40a itself. The eccentric portion is fitted to the inner circumferential side of the rotor 41a (so-called rolling piston). Therefore, when the driving shaft 40a rotates, the rotor 41a is eccentrically rotated along the inner peripheral surface of the tubular member 1a.

베인(42a)은 통형상 부재(1a)의 내주면에서 연장되어 로터(41a)의 외주면에 접하는 판상의 부재(판상 부재)이다. 베인(42a)은 스프링(43a)에 의해 통형상 부재(1a)의 내주면에서 돌출하여 구동축(40a)으로 향하는 힘을 받고 있으며, 이 힘으로 인해 베인(42a)의 선단은 로터(41a)의 외주면을 누르고 있다. 그리고 로터(41a)와 통형상 부재(1a) 사이에 형성되는 공간인 작동실(5a)은 로터(41a)의 외주면을 누르는 베인(42a)에 의해 구분된다.The vane 42a is a plate-like member (plate-like member) extending from the inner peripheral surface of the tubular member 1a and in contact with the outer peripheral surface of the rotor 41a. The vane 42a protrudes from the inner circumferential surface of the tubular member 1a by the spring 43a and receives a force directed toward the drive shaft 40a and the tip of the vane 42a is pressed against the outer peripheral surface of the rotor 41a . The operating chamber 5a which is a space formed between the rotor 41a and the cylindrical member 1a is divided by a vane 42a that presses the outer peripheral surface of the rotor 41a.

흡입구(13a)는 통형상 부재(1a)의 내주면에 마련된 개구부이며, 외부에서 작동실(5a)로 냉매 가스를 흡입시킨다. 작동부(4a)가 화살표 D2를 따라서 시계방향으로 회전하면 로터(41a)의 외주면에 의해 구분된 작동실(5a)의 공간은 통형상 부재(1a)의 내주면을 따라서 시계방향으로 이동한다. 토출구(14a)는 작동실(5a)의 내압이 정해진 토출압 미만일 때, 토출 밸브(15a)에 의해 폐쇄되어 있다. 작동실(5a)의 내압이 토출압 이상이 되었을 때, 토출구(14a)에서 냉매 가스가 토출된다.The suction port 13a is an opening provided in the inner peripheral surface of the tubular member 1a and sucks the refrigerant gas from the outside into the operation chamber 5a. When the operating portion 4a rotates clockwise along arrow D2, the space of the operating chamber 5a divided by the outer circumferential surface of the rotor 41a moves clockwise along the inner circumferential surface of the tubular member 1a. The discharge port 14a is closed by the discharge valve 15a when the internal pressure of the operation chamber 5a is less than the predetermined discharge pressure. When the internal pressure of the operation chamber 5a becomes equal to or higher than the discharge pressure, the refrigerant gas is discharged from the discharge port 14a.

본 변형예에서도 상기 실시형태와 마찬가지로 로터(41a)의 스러스트면에 마련된 수지층에 동심원을 이루는 복수의 고리형상 홈을 형성함으로써 수지층과 제1 폐쇄 부재 및 제2 폐쇄 부재 사이에 유막이 형성되기 쉽다. 단, 본 변형예에서는 로터(41a)가 편심 회전하기 때문에, 홈의 고리의 중심 위치와는 무관하게 쐐기 효과가 발생한다. 따라서 본 변형예에서는 홈의 고리의 중심 위치는 한정되지 않는다.In this modified example, a plurality of concentric annular grooves are formed in the resin layer provided on the thrust surface of the rotor 41a to form an oil film between the resin layer and the first closing member and the second closing member easy. However, in this modification, since the rotor 41a rotates eccentrically, a wedge effect is generated irrespective of the center position of the loop of the groove. Therefore, in this modification, the center position of the groove of the groove is not limited.

2-3. 변형예 22-3. Modification 2

도 7은 로터리형 유체 기계의 변형예를 도시한 도면이다. 이 경우, 통형상 부재(1b)의 내주면에는 요동 부시(bush)(45b)가 마련되어 있다. 작동부(4b)는 구동축(40b) 및 로터(41b)를 가진다. 로터(41b)는 이른바 스윙 피스톤이며, 판상의 부재(이하 "판상 부재(412b)"라고 함)와 원통형상의 기재(이하 "원통형상 기재(411b)"라고 함)를 가지며, 판상 부재(412b)는 요동 부시(45b)에 끼어서 기밀성이 유지되고 있다. 즉, 판상 부재(412b)는 원통형상 기재(411b)와 일체로 마련되며, 원통형상 기재(411b)의 외주면에서 통형상 부재의 내주면을 향해 연장되고, 그 내주면에 마련된 요동 부시(45b)에 끼인다. 로터(41b)와 통형상 부재(1b)의 내주면 사이에는 도 7에 도시한 것과 같은 작동실(5b)이 있으며, 이 작동실(5b)은 판상 부재(412b)에 의해 구분지어진다.Fig. 7 is a view showing a modification of the rotary fluid machine. Fig. In this case, a swing bush 45b is provided on the inner peripheral surface of the tubular member 1b. The operating portion 4b has a drive shaft 40b and a rotor 41b. The rotor 41b is a so-called swing piston and has a plate-like member (hereinafter referred to as a "plate-shaped member 412b") and a cylindrical substrate (hereinafter referred to as a "cylindrical substrate 411b" The airtightness is maintained by being caught by the swing bush 45b. That is, the plate-like member 412b is integrally provided with the cylindrical base material 411b and extends from the outer circumferential face of the cylindrical base material 411b toward the inner circumferential face of the tubular member and is engaged with the swing bush 45b provided on the inner circumferential face of the cylindrical base material 411b I will. An operating chamber 5b as shown in Fig. 7 is provided between the rotor 41b and the inner peripheral surface of the tubular member 1b. The operating chamber 5b is divided by the plate member 412b.

구동축(40b)은 편심부를 가지며, 이 편심부가 로터(41b)의 원통형상 기재(411b)의 내주면에 끼워넣어져 있기 때문에, 구동축(40b)이 회전하면 로터(41b)가 요동한다. 이에 따라, 판상 부재(412b) 및 원통형상 기재(411b)에 의해서 작동실(5b)이 구분되는 위치가 이동하고, 구분된 각 방을 각각 채우는 유체는 흡입구(13b)에서 토출구(14b)로 이동하여, 작동실(5b)의 내압이 상승하여 토출압을 넘어섰을 때 토출 밸브(15b)에 대항하여 토출구(14b)에서 토출된다.Since the drive shaft 40b has an eccentric portion and the eccentric portion is fitted in the inner peripheral surface of the cylindrical base 411b of the rotor 41b, the rotor 41b rocks when the drive shaft 40b rotates. Thus, the position at which the operation chamber 5b is divided by the plate-shaped member 412b and the cylindrical substrate 411b is moved, and the fluid filling each of the divided rooms is moved from the suction port 13b to the discharge port 14b And is discharged from the discharge port 14b against the discharge valve 15b when the internal pressure of the operating chamber 5b rises and exceeds the discharge pressure.

한편, 도 7에서 통형상 부재(1b)는 전체를 도시하지 않고 그 부분(내주면, 흡입구(13b), 토출구(14b), 토출 밸브(15b))을 도시하였다. 또한 요동 부시(45b)가 유지하는 판상 부재(412b)에서도 기밀성을 확보하기 위해, 요동 부시(45b)와 판상 부재(412b)가 존재하는 범위에 오목부를 마련하여, 수지층을 형성하면 더욱 바람직하다. 또한 통형상 부재(1b)의 형상은 원통형상이었으나 원통형상에 한정되지 않으며, 통형상이라면 예를 들면 단면이 타원이어도 된다.7, the tubular member 1b does not show the entirety, but shows its portion (inner circumferential surface, suction port 13b, discharge port 14b, discharge valve 15b). Further, in order to secure the airtightness in the plate member 412b held by the swing bush 45b, it is more preferable to form the resin layer by providing concave portions in the range where the swing bush 45b and the plate member 412b are present . Further, the shape of the tubular member 1b is cylindrical, but it is not limited to the cylindrical shape, and if it is cylindrical, for example, the cross section may be elliptical.

본 변형예에서도 상기 실시형태와 마찬가지로 원통형상 기재(411b)의 스러스트면에 마련된 수지층에 동심원을 이루는 복수의 고리형상 홈을 형성함으로써, 수지층과 제1 폐쇄 부재 및 제2 폐쇄 부재 사이에 유막이 형성되기 쉬워진다. 단, 본 변형예에서는 원통형상 기재(411b)가 요동하므로 홈의 고리의 중심 위치와 무관하게 쐐기 효과가 발생한다. 따라서 본 변형예에서는 홈의 고리의 중심 위치는 한정되지 않는다.In this modified example, a plurality of concentric annular grooves are formed in the resin layer provided on the thrust surface of the cylindrical base material 411b in the same manner as in the above-described embodiment, so that the oil film is formed between the resin layer and the first and second closing members Is easily formed. However, in the present modification, the cylindrical base material 411b is oscillated, so that a wedge effect is generated irrespective of the center position of the loop of the groove. Therefore, in this modification, the center position of the groove of the groove is not limited.

2-4. 변형예 32-4. Modification 3

도 8은 홈(C)의 변형예를 도시한 도면이다. 이 예에서 홈(C)의 폭(w)은 홈(C)끼리의 간격(p)보다 작다(w＜p). 산부(B)에는 홈(C)끼리의 사이에서 폭(a)을 가지는 평탄면이 마련되어 있다. 이 경우, 폭(a)은 폭(w)보다 작은(a＜w) 것이 바람직하다. 폭(a)을 폭(w)보다 작게 함으로써, 작동부(4)와 접촉하여 탄성 변형된 산부(B)에 의해 홈(C)이 완전히 메워져 버리는 일이 없다. 즉, 산부(B)가 홈(C)을 향해 탄성 변형되었다고 해도 홈(C)이 윤활유(80)를 유지하므로, 로터리형 유체 기계의 기밀성이 향상된다.Fig. 8 is a view showing a modified example of the groove C; Fig. In this example, the width w of the groove C is smaller than the interval p between the grooves C (w <p). The crest B is provided with a flat surface having a width a between the grooves C. As shown in Fig. In this case, the width a is preferably smaller than the width w (a <w). When the width a is made smaller than the width w, the grooves C are not completely buried by the elastically deformed peak portions B in contact with the actuating portion 4. [ That is, even if the crest B is elastically deformed toward the groove C, the groove C maintains the lubricant 80, so that the airtightness of the rotary type fluid machine is improved.

또한 홈(C)의 깊이(h)는 이웃하는 홈(C)들의 간격(p)보다 작은(h＜p) 것이 바람직하다. 이 경우, 이웃하는 홈(C)들 사이에 형성되는 산부(B)는 홈(C)의 깊이(h)에 해당하는 높이보다 간격(p)에 해당하는 기슭(foot) 부분의 폭이 길어지므로, 도 8의 가로방향의 힘에 대해 비교적 튼튼한 형상이 된다. 깊이(h)는 예를 들면 1~20㎛이다.It is also preferable that the depth h of the groove C is smaller than the interval p of the adjacent grooves C (h &lt; p). In this case, since the width of the foot portion corresponding to the interval p is longer than the height corresponding to the depth h of the groove C in the peak portion B formed between adjacent grooves C , It becomes a relatively strong shape with respect to the force in the transverse direction of Fig. The depth h is, for example, 1 to 20 占 퐉.

2-5. 변형예 42-5. Modification 4

전술한 실시형태에서 구동축(40)에 수직인 평면에 있어서 기재(411)의 단면 형상은 원형이었지만, 기재(411)의 단면 형상은 원형에 한정되지 않는다. 기재(411)의 단면 형상은 예를 들면 타원형이어도 되고, 뢸로 다각형과 같은 정폭 도형이어도 되며, 또한 반원과 타원을 조합한 형상이어도 된다.In the above-described embodiment, the cross-sectional shape of the base material 411 in the plane perpendicular to the drive shaft 40 is circular, but the cross-sectional shape of the base material 411 is not limited to a circular shape. The cross-sectional shape of the substrate 411 may be, for example, an elliptical shape, a constant width shape such as a polygonal shape, or a shape obtained by combining a semicircle and an ellipse.

2-6. 변형예 52-6. Modification 5

전술한 실시형태에서 홈(C)은 동심원을 이루는 고리형상 홈이었으나, 홈(C)은 소용돌이형상이어도 된다. 이 경우, 홈(C)의 소용돌이의 중심이 로터(41)의 회전 중심과 일치해도 쐐기 효과가 발생하므로, 홈(C)의 소용돌이의 중심이 로터(41)의 회전 중심과 일치해도 된다. 단, 홈(C)의 소용돌이의 중심이 로터(41)의 회전 중심과 다른 것이 전체적으로 쐐기 효과가 커지므로, 홈(C)의 소용돌이의 중심이 로터(41)의 회전 중심과 다른 것이 바람직하다. 또한 로터(41)의 회전 중심에 대한 홈(C)의 소용돌이의 중심의 편심량은 홈(C)의 소용돌이의 피치 1개분 이상인 것이 바람직하다(단, 홈(C)의 소용돌이의 속도가 일정한 경우).In the above-described embodiment, the groove C is an annular groove having a concentric circle, but the groove C may have a spiral shape. In this case, since the wedge effect occurs even if the center of the vortex of the groove C coincides with the center of rotation of the rotor 41, the center of the vortex of the groove C may coincide with the center of rotation of the rotor 41. [ It is preferable that the center of the vortex of the groove C is different from the center of rotation of the rotor 41 because the center of the vortex of the groove C is different from the center of rotation of the rotor 41 as a whole. It is preferable that the eccentric amount of the center of the vortex of the groove C with respect to the rotation center of the rotor 41 is equal to or larger than one pitch of the vortex of the groove C (provided that the velocity of the vortex of the groove C is constant) .

2-7. 변형예 62-7. Modification 6

전술한 실시형태에서는 수지층(410)에서 복수의 홈(C)이 형성되는 범위에 대해 언급하지 않았지만 수지층(410)의 전체면에 홈(C)이 형성되어 있지 않아도 되며, 수지층(410)의 일부에 홈(C)이 형성되어 있어도 된다. 또한 2개의 스러스트면에 마련된 수지층(410) 중 한쪽에 홈(C)이 형성되어 있어도 된다.The grooves C may not be formed on the entire surface of the resin layer 410 and the resin layer 410 may be formed on the entire surface of the resin layer 410. In this case, The grooves C may be formed in a part of the grooves. Further, grooves C may be formed in one of the resin layers 410 provided on the two thrust surfaces.

1: 통형상 부재 13: 흡입구
14: 토출구 15: 토출 밸브
2: 제1 폐쇄 부재 3: 제2 폐쇄 부재
4: 작동부 40: 구동축
41: 로터 410: 수지층
411: 기재 42: 베인(판상 부재)
44: 베인 홈 5: 작동실(공간)
6: 압축 기구 7: 모터
80: 윤활유 81: 볼트
9: 로터리형 압축기 B: 산부
C: 홈1: tubular member 13: inlet
14: Discharge port 15: Discharge valve
2: first closing member 3: second closing member
4: operation part 40: drive shaft
41: rotor 410: resin layer
411: base material 42: vane (plate material)
44: Vane groove 5: Working chamber (space)
6: compression mechanism 7: motor
80: Lubricating oil 81: Bolt
9: Rotary type compressor B:
C: Home

Claims (3)

통형상 부재와 상기 통형상 부재의 축방향의 양단의 개구부를 폐쇄하는 폐쇄 부재로 형성된 공간에 수용되며, 상기 축방향과 동일 방향의 축의 주위를 회전하는 기재(基材);
상기 기재의 스러스트면(thrust surface)에 형성된 수지층; 및
상기 수지층에 형성된 동심원을 이루는 복수의 고리형상 홈 또는 소용돌이형상 홈으로서, 상기 고리형상 홈의 고리 중심 또는 상기 소용돌이형상 홈의 소용돌이의 중심이 상기 기재의 회전 중심과 다른 홈;을 포함하는 로터.A base member accommodated in a space defined by a tubular member and a closing member closing an opening at both ends in the axial direction of the tubular member and rotating around an axis in the same direction as the axial direction;
A resin layer formed on the thrust surface of the substrate; And
A plurality of concentric annular grooves or spiral grooves formed in the resin layer, wherein the center of the ring of the annular groove or the center of the spiral of the spiral groove is different from the center of rotation of the base. 제1항에 있어서,
상기 기재의 회전 중심에 대한 상기 고리형상 홈의 고리의 중심의 편심량 또는 상기 소용돌이형상 홈의 소용돌이의 중심의 편심량이 상기 홈의 피치 이상인 로터.The method according to claim 1,
Wherein an eccentric amount of the center of the annular groove of the annular groove with respect to the rotational center of the base material or an eccentric amount of the center of the vortex of the spiral groove is equal to or greater than a pitch of the groove. 통형상 부재;
상기 통형상 부재의 축방향의 양단의 개구부를 폐쇄하는 폐쇄 부재; 및
제1항 또는 제2항에 기재된 로터;를 포함하는 로터리형 유체 기계.A tubular member;
A closing member closing the openings at both ends in the axial direction of the tubular member; And
A rotary type fluid machine comprising the rotor according to claim 1 or 2.
KR1020157034744A 2014-02-21 2015-02-19 Rotor and rotary fluid machine KR101629899B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2014032141A JP6225045B2 (en) 2014-02-21 2014-02-21 Rotor and rotary fluid machinery
JPJP-P-2014-032141 2014-02-21
PCT/JP2015/054668 WO2015125888A1 (en) 2014-02-21 2015-02-19 Rotor and rotary fluid machine

Publications (2)

Publication Number Publication Date
KR20150143886A KR20150143886A (en) 2015-12-23
KR101629899B1 true KR101629899B1 (en) 2016-06-13

Family

ID=53878385

Family Applications (1)

Application Number Title Priority Date Filing Date
KR1020157034744A KR101629899B1 (en) 2014-02-21 2015-02-19 Rotor and rotary fluid machine

Country Status (6)

Country Link
US (1) US9835157B2 (en)
EP (1) EP3037666B1 (en)
JP (1) JP6225045B2 (en)
KR (1) KR101629899B1 (en)
CN (2) CN107448386B (en)
WO (1) WO2015125888A1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6382877B2 (en) * 2016-03-24 2018-08-29 大豊工業株式会社 Vane pump
JP6704309B2 (en) * 2016-07-27 2020-06-03 日立グローバルライフソリューションズ株式会社 Hermetic compressor
CN106949061A (en) * 2017-04-28 2017-07-14 广东美芝制冷设备有限公司 Rotary compressor and its pump housing
CN110067752A (en) * 2019-04-17 2019-07-30 耐力股份有限公司 A kind of new energy oil-free sliding vane type air compressor machine
JP6988932B2 (en) * 2020-01-29 2022-01-05 株式会社富士通ゼネラル Rotary compressor

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008051018A (en) * 2006-08-25 2008-03-06 Denso Corp Scroll compressor

Family Cites Families (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4730008Y1 (en) * 1970-02-20 1972-09-08
JPS4730008U (en) * 1971-04-30 1972-12-05
JPS5518545Y2 (en) * 1975-10-03 1980-04-30
JPS5479809A (en) * 1977-12-07 1979-06-26 Seiko Instr & Electronics Ltd Gas compressor
JPS5735187A (en) * 1980-08-08 1982-02-25 Diesel Kiki Co Ltd Vane type compressor
JP3166258B2 (en) * 1991-08-07 2001-05-14 ダイキン工業株式会社 Rotary compressor
US5310326A (en) * 1992-09-14 1994-05-10 Mainstream Engineering Corporation Rotary compressor with improved bore configuration and lubrication system
JP2004278309A (en) 2003-03-12 2004-10-07 Calsonic Compressor Seizo Kk Gas compressor
JP2004316533A (en) * 2003-04-16 2004-11-11 Matsushita Electric Ind Co Ltd Rotary compressor
KR20050066322A (en) * 2003-12-26 2005-06-30 삼성전자주식회사 Compressor
US7878777B2 (en) 2006-08-25 2011-02-01 Denso Corporation Scroll compressor having grooved thrust bearing
WO2009066413A1 (en) * 2007-11-21 2009-05-28 Panasonic Corporation Compressor integral with expander
JP2010133317A (en) * 2008-12-04 2010-06-17 Panasonic Corp Hermetic compressor
JP2012062763A (en) * 2010-09-14 2012-03-29 Taiho Kogyo Co Ltd Rotary type compressor
CN102454610A (en) * 2010-10-27 2012-05-16 乐金电子(天津)电器有限公司 Piston structure for closed type compressor
JP5041059B2 (en) * 2010-12-27 2012-10-03 ダイキン工業株式会社 Compressor
ES2660014T3 (en) 2010-12-22 2018-03-20 Daikin Industries, Ltd. Compressor
JP2012137009A (en) * 2010-12-27 2012-07-19 Daikin Industries Ltd Compressor
JP2012137008A (en) * 2010-12-27 2012-07-19 Daikin Industries Ltd Compressor
US9243635B2 (en) * 2010-12-27 2016-01-26 Daikin Industries, Ltd. Compressor with different resin hardness layers
JP5767959B2 (en) * 2011-12-22 2015-08-26 大豊工業株式会社 Sliding member
CN203130518U (en) * 2013-02-04 2013-08-14 安徽美芝精密制造有限公司 Low backpressure rotating compressor and piston thereof
JP6012574B2 (en) * 2013-09-27 2016-10-25 大豊工業株式会社 Scroll member and scroll type fluid machine

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008051018A (en) * 2006-08-25 2008-03-06 Denso Corp Scroll compressor

Also Published As

Publication number Publication date
EP3037666A4 (en) 2016-10-19
JP6225045B2 (en) 2017-11-01
US20160108916A1 (en) 2016-04-21
CN105392994A (en) 2016-03-09
CN105392994B (en) 2017-09-01
WO2015125888A1 (en) 2015-08-27
KR20150143886A (en) 2015-12-23
CN107448386B (en) 2019-03-22
EP3037666B1 (en) 2018-10-10
EP3037666A1 (en) 2016-06-29
US9835157B2 (en) 2017-12-05
CN107448386A (en) 2017-12-08
JP2015158143A (en) 2015-09-03

Similar Documents

Publication Publication Date Title
KR101629899B1 (en) Rotor and rotary fluid machine
US9605676B2 (en) Variable speed scroll compressor
CN109209866B (en) Compressor with floating seal
US10443654B2 (en) Bearing and scroll-type fluid machine
US9752579B2 (en) Scroll member and scroll-type fluid machine
JP7010202B2 (en) Fluid machine
JP2006097619A (en) Compressor
JP5728058B2 (en) Rotary fluid machine
JP6317932B2 (en) Rolling piston member and rotary fluid machine
US4558999A (en) Vane type pump device
JP2015158144A (en) rolling piston and rotary type fluid machine
KR101865174B1 (en) Device for compressing a gaseous fluid
EP2857688B1 (en) Rotary compressor
KR20230172234A (en) Reciprocating compressor
KR100323543B1 (en) Friction Reduction Device for Rotary Compressor
EP3872348A1 (en) Oil supply mechanism of rotating machinery and rotating machinery having oil supply mechanism
KR200392234Y1 (en) Rotary compressor with reducing friction function
JPH0512684U (en) Vane pump
KR20030003445A (en) Friction reduce structure for rotary comrressor
US20100232987A1 (en) Variable displacement inclined plate type compressor

Legal Events

Date Code Title Description
A201 Request for examination
A302 Request for accelerated examination
E902 Notification of reason for refusal
E701 Decision to grant or registration of patent right
GRNT Written decision to grant
FPAY Annual fee payment

Payment date: 20190515

Year of fee payment: 4